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WO1997035104A1 - Moteur a pistons libres et son mode de fonctionnement - Google Patents

Moteur a pistons libres et son mode de fonctionnement Download PDF

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Publication number
WO1997035104A1
WO1997035104A1 PCT/BY1997/000001 BY9700001W WO9735104A1 WO 1997035104 A1 WO1997035104 A1 WO 1997035104A1 BY 9700001 W BY9700001 W BY 9700001W WO 9735104 A1 WO9735104 A1 WO 9735104A1
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WO
WIPO (PCT)
Prior art keywords
energy
hydraulic
power plant
fuel
liquid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/BY1997/000001
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English (en)
Inventor
Evgeny Alexandrovich Starodetko
Georgy Evgenievich Starodetko
Konstantin Evgenievich Starodetko
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Individual
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Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AU18638/97A priority Critical patent/AU1863897A/en
Publication of WO1997035104A1 publication Critical patent/WO1997035104A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B71/00—Free-piston engines; Engines without rotary main shaft
    • F02B71/04—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby
    • F02B71/045—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby with hydrostatic transmission

Definitions

  • the invention relates to machine power plant and may be used in automotive industry because it concerns the means providing an adaptation of engine and means, accumulating energy, to automobile modes
  • the object accepted as a prototype in part of machine power plant operation method represents method, what air and fuel mixture is burnt in a cylinder with movable piston at, working gases heat energy transformed in mechanical one and the last is transferred to actuator with use of compressed liquid hydraulic energy, at this part of energy is used for air compression, conducted in cylinder
  • the method In part of power plant operation regulation accepted as prototype the method consists in energy quantity change produced by engine by means of quantity change of fuel conducted in cylinder, in fraction of energy accumulation for usage as it becomes necessary and in transfer to actuator of such energy quantity, that required to it for useful work production
  • the object represents a machine power plant. containing engine piston with installed in it differential piston, hydraulic system, including hydraulic pump with drive from differential piston, hydraulic motor, hydraulic accumulator, pipe-line and valves, supplv and fuel ignition device, air compression device, as well control svstem. joined to valves and provided with position transducers
  • the proposed invention task is an elaboration of engine operation method and transfer regulation of its energy on wheels by means of adaptation in correspondence with engine characteristics and single regimes of its maintenance on automobile, vehicle drive complex scheme creation, capable to provide, at condition of minimum fuel consumption achievement, rotational first and second energy sources consumption at motion, including friction forces. aerodynamic resistance, inertia and gravity forces overcoming.
  • the drive efficiency is determined mainly with engine characteristics, that works most efficiently at definite parameters combination, considerably influences on engine indicator efficiency and mechanical losses.
  • the power plant for these methods realization contains the engine cylinder with installed a differential piston in it, hydraulic system, including hydraulic pump with drive from differential piston, hydraulic motor, hydraulic accumulator, pipe-lines and valves, supply and fuel ignition device, air compression device as well control system joined to valves and equipped with position transducers, at this in accordance with invention, air compression device is realized with drive from intermediate differential piston stage and provided with receiver and cylinder volume of air compression device is practised in 1,5.. 3,0 times less than engine cylinder volume, and besides in variance the air compression device is realized as two- stage and device first stage cylinder volume is practised in 1,5 . 3,0 times less than engine cylinder volume.
  • control system is realized as programmed, position transducers are installed on actuator and valves are switched to system, installed on gases exhaust from engine cylinder, intake in this cylinder of compressed air and fuel, on output from hydraulic pump and on input in hydraulic motor.
  • the power plant may be realized with location in one engine cylinder of two differential pistons installed in opposite manner.
  • the fuel, burnt in engine cylinder, at this ignition and fuel supply device may be joined with hydraulic accumulator through intermediate capacity, equipped with rebound valve.
  • the invention envisages realization variants, at which several hydraulic motors are switched to one hydraulic accumulator through separate valves, switched to control system, or several hydraulic accumulators are switched to single hydraulic motor through switch connected to control system or several hydraulic motors are switched to several hydraulic accumulator through hydraulic selector point to control system.
  • the distinguishing peculiarity of claimed invention is a fact, that in every cycle the fuel in engine cylinder is burnt at the same process parameters, at this hydraulic energy is produced, stored and transferred as an internal energy of deformed liquid.
  • the fuel combustion process parameters constancy that is the same in every working cycle fuel quantity, compressed air quantity and parameters, combustion chamber volume and working gases volume in its expansion end, correspondingly, constancy for working gases in every cycle of temperatures and pressure, as maximum so final, permit to realize fuel combustion at optimal regime for extraction of its chemical energy, that is to receive maximum possible energy quantity from consumed fuel.
  • receiving and subsequent energy transfer as deformed liquid energy that may be stored so long as You want, permit to transform hot working gases energy defied to prolong storage in deformed liquid easily controlled and long- stored energy, that gives possibility to burn fuel only for automobile motion unreversible resistance overcoming and losses replenishment of stored energy, providing by this minimum fuel consumption.
  • the other distinguishing peculiarity of claimed operation method is a fact, that air is compressed and liquid is deformed at first at the expense of working gases energy, and then at the expense of moving piston mass energy, at this air is compressed outside of engine cylinder till fuel combustion ignition parameters.
  • the air compression till fuel ignition parameters outside engine cylinder permits to provide not only optimal parameters in cylinder for every fuel combustion cycle, but come to the principally new power plant operation regulation method, so as at present in any moment compressed air and corresponding fuel dose the working process in engine cylinder also may be realized in any time moment.
  • the compressed air parameters maintenance sufficient for fuel combustion ignition permits not only to liberate ICE cylinders from work to prepare a fresh charge, but in any automobile motion moment it's possible to supply fuel and receive from its combustion the required work, that is easily change engine cycle frequency, that expands the technological possibilities of claimed plant.
  • the engine is capable to adapt to external loads correspondingly changing operation cycles frequency.
  • the power plant for claimed method realization besides elements, providing fulfillment of functions considered above, that may be realized by already known means, has additionally its distinguishing pecula ⁇ ties namely, in claimed plant the air compression device is made with drive from differential piston intermediate stage and supplied with receiver at this the air compression device cvhnder is practised in 1,5 3 0 times lower than engine cylinder volume
  • the presence of volume for working gases expansion in 1,5 3,0 times greater than suction and supplied later air volume in cylinder permits to receive the working gases prolonged expansion, to achieve such its parameters on exhaust, at which completely used the energy and provided sufficient exhaust pu ⁇ ty
  • the same exhaust conditions may be provided in execution variant at which the air compression device is fulfilled as two-stage, at this the device first stage cvhnder volume is practised in 1,5 3,0 times less than engine cylinder volume In this variant it's possible to achieve more high compressed air pressure, supplied in engine cylinder and realized in the last Diesel cycle
  • the claimed regulation method is realized at the expense of control system distinguishing pecula ⁇ ty, that executed as programmed, at this position transducers are installed on actuator and valves are switched to system, installed on gases exhaust from engine cylinder on supply in this cylinder of compressed air and fuel, on output from hydraulic pump and on input in hydraulic motor
  • the presence of controlled valves permits to organize the energy transfer between pump and hydraulic motor through hydraulic accumulator and to regulate the transferred energy power bv means of working strokes number variation So as a single fuel dose combustion, and at the same parameters a constant energy quantity is produced, a power value transferred w ith one deformed liquid pulse, is a constant value In any hvdrauiic transmission line of claimed power plant either there is deformed liquid pulse or it absents.
  • the fuel usage hydraulic system working liquid resolves not only power plant lubrication problem, but the hydraulic system liquid degrading problem, so as at engine operation the liquid in hydraulic system is contineosly renewed.
  • the proposed technical solution of fuel supply considerably simplifies the known fuel supply system, does not require of additional pumps, distinguishes with control simplicity, that is caused by namely a fact, that in claimed method the fuel dose burnt in every working cycle - the constant value.
  • claimed power plant may be realized in different variants, realizing claimed operation method and regulation, in engine cylinder two differential pistons may be installed, situated oppositely, to one hydraulic accumulator several hydraulic motors are switched through separate, switched to control system valves, to single hydraulic motor several hydraulic accumulators are switched through separate switched to control system valves, to several hydraulic accumulators are switched several hydraulic motors through hydraulic switch joined to control system.
  • a hydraulic motor may be switched, driving in operation an electric current generator or energy accumulator in form of flywheel. All this variants extend invention usage technological possibilities.
  • the cited power plant execution variants are possible namely to fact, that in invention the pulse hydraulic energy transfer is used, so as energy received from working gases is transformed in deformed liquid energy, so at every fuel combustion tact the single liquid deformation pulse is received, that afterwards is stored so long as You want in hydraulic accumulator and is used in hydraulic motor as far as need.
  • the energy transfer by means of deformed liquid pulse is fulfilled on a single hydraulic line.
  • the hydropulse transmission provides the energy consumer and motor interaction in conditions of pure hydraulic tie, at absence of transferring shafts, gears, levels and other mechanical links.
  • the energy generator and consumer may change roles at this, that provides of energy recuperation, directing it in accumulator.
  • the flywheel or reversible electrical machine driving mechanism and vehicuie wheel may serve as " generator - consumer" couple.
  • the claimed invention provides the interaction between source and mechanical energy receiver at the expense of liquid deformation and pipe-line, which it is included in, that considerably expands technological possibilities of such energy transfer
  • At rotation transfer deformed liquid pulses may be transferred on more than one hydraulic line with pulse transfer time moment shift on angle of source and consumer mechanisms revolution on value multiple to hydraulic lines number, that provides dead points absence at rotative moment transfer.
  • pulse transfer time moment shift on angle of source and consumer mechanisms revolution on value multiple to hydraulic lines number that provides dead points absence at rotative moment transfer.
  • the rotative moment transfer uniformity on the wheel is the same as at asynchronous electric motor usage.
  • the machine power plant contains the engine cylinder 1 with the differential piston 2 installed in it, hydraulic system including hydraulic pump 3 with a drive from the differential piston 2, hydraulic motor 4, hydraulic accumulator 5, pipe-lines and controlled, equipped with drive valves and rebound valves performing due to the difference of pressure in corresponding environment
  • the plant also contains the supply and fuel ignition device 6, that in the case of the Diesel cycle (presented on draft) is an injector and in the case of the cycle with the lower compressed air pressure is a mixturer of the compressed air and fuel, equipped with an ignition plug, connected through the control system 8 to an elect ⁇ c voltage source
  • the plant contains the air compression device 7, the control system 8, connected to controlled valves with the use of corresponding drive and provided with position transducers 9 A.t this point the air compression device 7 is executed with drive from differential piston 2 intermediate stage and provided with receiver 10, and air compression device cylinder volume 7 is practised in 1,5 3,0 times less than engine 1 cylinder volume
  • the air compression device as two-stage with differential piston 2 additional stage providing, and between stages the intermediate receiver 1 1 is installed, at this cylinder volume of namely first device stage 7 is executed in 1,5 3,0 times less than engine 1 cylinder volume
  • the air intake and receivers 10, 1 1 are joined to air compression device 7 through rebound valves
  • the control system 8 is executed as programmed, position transducers 9 are installed on actuator - wheel 12, the actuator may be also anv energy accumulator - flywheel or reversible electric machine with elect ⁇ cal energy accumulator
  • two differential pistons 2 may be installed situated oppositely, at corresponding location and connection of other power plant elements analogous to presented on the draft
  • the fuel is used, burnt in engine cylinder, at this supply and fuel ignition device 6 is connected with hydraulic accumulator 5 through the intermediate capacity 18, equipped with rebound valve
  • the capacity 19 serves equipped with sp ⁇ ng-loaded piston 20, that is joined to hydraulic accumulator 5 through rebound valve
  • the claimed method of power plant operation we consider on example of scheme presented on the draft, which Diesel cycle is realized on, and that operates in the following way.
  • the plant hydraulic system Before operation inition the plant hydraulic system is completely filled with liquid fuel. filling it through capacity 19 throat. At this the piston 20 compresses the mechnical or gase spring and in hydraulic system the initial surplus pressure is created of order 0,5-1,0 atm. that provides absence of gas bubles in hydraulic system.
  • receiver 10 the compressed air stored at fuel combustion inition parameters in engine 1 cylinder.
  • the compressed air pressure in receiver 10 and pressure in the intermediate capacity 18 is provided during preceding engine operation or at first start is created from external source.
  • Controlled valves 13, 14, 15, 16, 17 are stand in position, presented on the draft The piston 2 at this comes in upper dead point of engine 1 cylinder.
  • the compressed air quantity is determined with cylinder 1 dead capacity volume, and fuel dose - with intermediate capacity volume. After this valves 14 and 15 are switched off. At mixing of fiiel with high pressure air the mixture self ignition takes place, fuel dose burns with working gases formation at maximum cycle temperature In variant of cycle realization with lower compressed air pressure in device 6 at valves 14 and 15 opening the mixing of compressed air and fuel is produced and mixture ignition with candle spark, generated on instruction from control system 8 Under action of working gases pressure the piston 2 is set in motion and besides in motion inition a pressure on piston differential surfaces from air compression device and hydraulic pump is little and piston moves with accelaration (on the draft from left to right) At piston motion the air compression takes place in compession device 7 stages and liquid ousting from hydraulic pump 3 cylinder through opened valve 16 The air entered in the first stage of device 7 from atmosphere is ousted in intermediate receiver 1 1 , and air at intermediate receiver pressure is ousted in receiver 10 The pressure of compressed air in receiver 10 achieves at this the value of order 100 atm
  • the received energy pulse is stored as elasticly deformed liquid in hydraulic accumulator 5 and in intermediate capacity 18 At this, in difference to working gases energy, that it ' s impossible to keep sufficeintly long time, the deformation energy may be kept as long as You want In intermediate capacity 18 at this the insignificant fraction of deformed energy is stored.
  • the intermediate capacity 18 volume consists value not more than 0.01-0.02 from hydraulic accumulator 5 volume. So as fuel combustion process parameters in cylinder 1 are constant. the intermediate capacity 18 volume is calculated in a such way that liquid, deformed in it at pulse production, represents the fuel dose for one working cycle, that value is also constant.
  • the control system 8 in correspondence with assigned by operator programme, with taking in account the actuator 12 position, controlled with transducer 9, and its functional assignment (automobile wheel, energy accumulator drive and so on) in necessary moment time proceeds the sygnal for valve 17 opening.
  • hydraulic accumulator 5 and hydraulic motor 4 are connected, at the expense of liquid deformation pulse hydraulic motor piston moves, accomplishing working stroke and transferring the energy to actuator 12. So as liquid volume value in hydraulic accumulator 5 and hydraulic motor 4 is less on fuel dose value, entered in the intermediate capacity 18, than liquid in hydraulic accumulator 5 and pump 3, the liquid pressure in hydraulic accumulator 5 is decreased less than pressure at hydraulic system filling, and from capacity 19 with piston 20 the additional liquid volume is ousted through rebound valve, compensating fuel consumption.
  • the piston 2 ousted by liquid moves in initial state (upper dead point of engine, the extreme left postion on the draft).
  • Exhausted gases through opened valve 13 are ejected, and through rebound valve and intake in the air compression device 7 the fresh charge entakes
  • device 7 execution as two-stage in its second stage the air enters from receiver 1 1 , compressed by first stage on the preceding working stroke.
  • At reaching by piston of its extreme position valves 13 and 17 close and the plant comes in initial state, waiting the next instruction from control system 8 programme.
  • the claimed plant provides the accelaration and breaking without energy losses
  • the claimed power plant operation regulation is realized with frequency variation of deformed liquid pulses produced with engine and/or deformed pulse transfer direction change from one of plant element to other. These variations are produced on sygnals from control system 8 as it was described above. Sygnals are produced by system 8 according to programme, assigned by operator, that takes in consideration actuators position, controlled by transducers 9, common machine maintenance parameters, for instance, automobile motion speed, necessity of its change and so on, as well position in concrete time moment of power plant elements in every hydraulic line.
  • the engine power may be regulated with fuel combustion frequency variation This is the principally new method, permitting to receive any beforhand assigned maximn power without cylinder variation and working mixture composition.
  • the scheme setting on concrete regime may be realized practically instantly (more exactly during one pumper stroke) at the expense of corresponding valves switching program modification.
  • the frequency principle of power control requires principally new working process organization, when ICE may stop produce mechanical energy on any step and on any other one - produce working stroke.
  • Such possibility is provided by compressed air reservation in receiver 10, that permits to realize power plant working process with built in ICE start process and provide the substantial rotative moment appearance at actuator 12 wheel rotation null speed. At frequency control the useful power may vary in very broad limits.
  • engine loading possibility "from start” we receive engine characteristics, that may work without gear box and clutch, that permits directly connect engine with wheel.
  • the frequency control is principally the programme control and may be realized with use of control system 8, executed on a base of microprocessor, that prepares working strokes execution programme similar to programme for machine tool with numerical control, when working strokes alteration is reflected by binary code.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

Mode de fonctionnement d'un moteur, procédé de régulation du fonctionnement d'un moteur, et moteur correspondant. On décrit un moteur utilisable, par exemple, dans l'industrie automobile. Afin de minimiser la consommation de carburant tout en assurant le transfert de l'énergie mécanique aux roues du véhicule, le moteur comporte un cylindre (1) dans lequel est monté un piston différentiel (2), un système hydraulique comprenant une pompe hydraulique (3) avec entraînement à partir d'un piston différentiel (2), un moteur hydraulique (4), et un accumulateur hydraulique (5). Ledit moteur comporte également un dispositif (6) d'admission et d'allumage du carburant, un dispositif de compression d'air (7), et un système de commande (8) équipé de transducteurs de position (9). Le dispositif de compression d'air (7) fonctionne à l'aide d'un épaulement intermédiaire du piston différentiel (2), et est relié à un récepteur (10). Le système de commande est programmé et les transducteurs de position (9) sont montés sur une roue à actionneurs (12). Des soupapes commandées sont traversées par les gaz d'échappement en provenance du cylindre (13) du moteur, et montées au niveau de l'orifice d'admission d'air (14) et de carburant (15) de ce cylindre, de l'orifice de sortie de la pompe hydraulique (16) et de l'orifice d'entrée du moteur hydraulique (17), et elles sont reliées au système à l'aide des actionneurs.
PCT/BY1997/000001 1996-03-20 1997-03-03 Moteur a pistons libres et son mode de fonctionnement Ceased WO1997035104A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU18638/97A AU1863897A (en) 1996-03-20 1997-03-03 Free piston engine and method of operating

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BY960121 1996-03-20
BY960121 1996-03-20

Publications (1)

Publication Number Publication Date
WO1997035104A1 true WO1997035104A1 (fr) 1997-09-25

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PCT/BY1997/000001 Ceased WO1997035104A1 (fr) 1996-03-20 1997-03-03 Moteur a pistons libres et son mode de fonctionnement

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AU (1) AU1863897A (fr)
RU (1) RU2117788C1 (fr)
WO (1) WO1997035104A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002055852A1 (fr) * 2000-12-18 2002-07-18 Caterpillar Inc. Systeme de moteur a pistons libres pourvu d'une sortie hydraulique a commande directe
WO2011046975A1 (fr) * 2009-10-12 2011-04-21 Sturman Digital Systems, Llc Moteurs à combustion interne hydrauliques
CN102748131A (zh) * 2011-06-03 2012-10-24 摩尔动力(北京)技术股份有限公司 无死态自由活塞发动机
US8887690B1 (en) 2010-07-12 2014-11-18 Sturman Digital Systems, Llc Ammonia fueled mobile and stationary systems and methods
CN104763525A (zh) * 2015-02-03 2015-07-08 北京理工大学 一种自吸式液压自由活塞直线发动机
US9206738B2 (en) 2011-06-20 2015-12-08 Sturman Digital Systems, Llc Free piston engines with single hydraulic piston actuator and methods
US9464569B2 (en) 2011-07-29 2016-10-11 Sturman Digital Systems, Llc Digital hydraulic opposed free piston engines and methods
RU2774925C1 (ru) * 2021-11-26 2022-06-27 Федеральное государственное бюджетное образовательное учреждение высшего образования "Ярославский государственный технический университет" ФГБОУВО "ЯГТУ" Гидропневмодвигатель внутреннего сгорания

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2327043C1 (ru) * 2006-12-27 2008-06-20 Закрытое акционерное общество "Метанол и азотные процессы" Свободнопоршневая машина
RU2396445C2 (ru) * 2008-09-17 2010-08-10 Бесарион Чохоевич Месхи Камерный двигатель маг
RU173896U1 (ru) * 2016-10-10 2017-09-18 Владимир Алексеевич Попов Свободнопоршневой двухтактный двигатель-гидронасос

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4599861A (en) * 1985-05-13 1986-07-15 Beaumont Richard W Internal combustion hydraulic engine
US4705460A (en) * 1985-02-26 1987-11-10 Anton Braun Bounce chambers for multi-cylinder linear engine compressors
EP0493135A1 (fr) * 1990-12-27 1992-07-01 HALL, Keith Gordon Moteur à combustion interne
WO1993010343A1 (fr) * 1991-11-19 1993-05-27 Innas B.V. Procede d'exploitation d'un moteur a pistons libres, et moteur a pistons libres associe

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU527524A1 (ru) * 1974-12-23 1976-09-05 Предприятие П/Я А-1697 Комбинированна силова установка

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4705460A (en) * 1985-02-26 1987-11-10 Anton Braun Bounce chambers for multi-cylinder linear engine compressors
US4599861A (en) * 1985-05-13 1986-07-15 Beaumont Richard W Internal combustion hydraulic engine
EP0493135A1 (fr) * 1990-12-27 1992-07-01 HALL, Keith Gordon Moteur à combustion interne
WO1993010343A1 (fr) * 1991-11-19 1993-05-27 Innas B.V. Procede d'exploitation d'un moteur a pistons libres, et moteur a pistons libres associe

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6470677B2 (en) 2000-12-18 2002-10-29 Caterpillar Inc. Free piston engine system with direct drive hydraulic output
GB2375144A (en) * 2000-12-18 2002-11-06 Caterpillar Inc Free piston engine system with direct drive hydraulic output
GB2375144B (en) * 2000-12-18 2005-02-16 Caterpillar Inc Free piston engine system with direct drive hydraulic output
WO2002055852A1 (fr) * 2000-12-18 2002-07-18 Caterpillar Inc. Systeme de moteur a pistons libres pourvu d'une sortie hydraulique a commande directe
DE112010004067B4 (de) 2009-10-12 2022-02-03 Sturman Digital Systems, Llc Hydraulische Brennkraftmaschinen
WO2011046975A1 (fr) * 2009-10-12 2011-04-21 Sturman Digital Systems, Llc Moteurs à combustion interne hydrauliques
CN102639842A (zh) * 2009-10-12 2012-08-15 斯德曼数字系统公司 液压内燃机
US8887690B1 (en) 2010-07-12 2014-11-18 Sturman Digital Systems, Llc Ammonia fueled mobile and stationary systems and methods
CN102748131A (zh) * 2011-06-03 2012-10-24 摩尔动力(北京)技术股份有限公司 无死态自由活塞发动机
US9206738B2 (en) 2011-06-20 2015-12-08 Sturman Digital Systems, Llc Free piston engines with single hydraulic piston actuator and methods
US9464569B2 (en) 2011-07-29 2016-10-11 Sturman Digital Systems, Llc Digital hydraulic opposed free piston engines and methods
CN104763525A (zh) * 2015-02-03 2015-07-08 北京理工大学 一种自吸式液压自由活塞直线发动机
RU2774925C1 (ru) * 2021-11-26 2022-06-27 Федеральное государственное бюджетное образовательное учреждение высшего образования "Ярославский государственный технический университет" ФГБОУВО "ЯГТУ" Гидропневмодвигатель внутреннего сгорания

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Publication number Publication date
AU1863897A (en) 1997-10-10
RU2117788C1 (ru) 1998-08-20

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